|Publication number||US7021510 B2|
|Application number||US 10/777,555|
|Publication date||Apr 4, 2006|
|Filing date||Feb 12, 2004|
|Priority date||Feb 12, 2004|
|Also published as||US20050179019|
|Publication number||10777555, 777555, US 7021510 B2, US 7021510B2, US-B2-7021510, US7021510 B2, US7021510B2|
|Inventors||David Irwin Ellingson|
|Original Assignee||David Irwin Ellingson|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (16), Referenced by (26), Classifications (18), Legal Events (5)|
|External Links: USPTO, USPTO Assignment, Espacenet|
This invention relates to the field of high force cable retraction means. Present devices generally utilize spool winding methods. These are limited in the amount of cable that can be retracted (only until the spool is full). Spool winding is also limited in maximum retraction force due to cable damage. The high force retraction causes excessive cable stress from bending and squeezing between the windings on the spool.
Rotating sheaves such as used for elevators cannot provide high force retraction. Elevators overcome this deficiency with counterweights and by utilizing multiple cables.
This invention further relates to a continuous cable pulling device (no limit on pulling length.) U.S. Pat. No. 4,256,199 granted to Sellards shows a serpentine device. This device is limited due to the high bending strains imposed on the cable. U.S. Pat. No. 5,009,353 granted to Alquist shows a continuous loop friction device. This device cannot provide a high normal force needed to achieve high pulling force. U.S. Pat. No. 4,456,226 granted to Stumpmeier shows a piston operated device to provide step action cable retraction. This intermittent motion limits the speed of the traction device and imparts repetitive accelerations on the cable. U.S. Pat. No. 5,082,248 granted to Harig shows a grooved bull wheel device with a continuous looping pressure chain. This apparatus provides continuous cable pulling. With additional pressure chains, the apparatus would also be capable of high pulling force. The disadvantages remaining would include the 360 degree cable bending arc, complexity, risk of the cable coming out of the bull wheel groove, and difficulty in threading cable through the apparatus.
The present invention further relates to gondola movement on a cable. The cable traction apparatus would be the motive force to cause movement of the gondola along the cable. In this configuration, the traction apparatus is affixed to the gondola and the cable is stationary.
The object of the invention is to provide a continuous and high force cable pulling mechanism. Two key systems are at work to accomplish this objective. The first system is a power linkage that converts rotary engine power to lineal force along the axis of the cable. This power linkage could consist of a group of gears, chain drives, belts, pneumatics, hydraulics or other power devices. A looping chain is used to apply this lineal force in a continuous manner. The second system provides the transfer of this lineal force to the cable. Frictional force is defined as the coefficient of friction times the normal force. The chain to cable coefficient of friction is nominally bounded by the materials used for the chain and cable. A reasonable clean steel to steel surface has a coefficient of friction of about 0.7 and is generally not able to be dramatically increased. A more direct method to dramatically increase the friction force is to increase the normal force. A group of rollers are used to provide the high normal force.
The moving chain links have a concave surface that matches the radius of the cable. This allows the high normal force to be distributed over a larger area. The limiting factor for normal force is to not exceed the stress deformation limit of the cable that is resisting this force. The cable is surrounded with two or more links—thus exerting even pressure completely around the cable. The normal force is applied to the chain links through pressure rollers. The pressure rollers and links are staggered in such a way that the force of the pressure roller is always distributed over a substantial area on the cable. This allows a much higher normal force to be applied without damaging the cable. The rollers are biased with Belleville springs. These springs are adjustable and provide a very high force over a short range of movement.
The invention includes several unique features as part of the mechanism. The multiple chain drives surround the cable. The drive line to bring this power to the chains from a single engine is accomplished in a unique manner. A worm drive pinion is positioned in a manner to allow the cable to run through the center of this pinion. Multiple worm output gears (one for each chain drive) are driven by this worm drive pinion. This gearing method keeps the multiple chain drives synchronized and reduces the number of parts required. The synchronization is required to maintain the staggered links.
The straight line path of the cable through the mechanism allows a smaller diameter pilot cable to freely pass through the device. The mechanism self engages the traction cable when it first contacts the moving chain links.
Further features include methods to maintain the optimum coefficient of friction between the chain links and cable.
The power linkage for this apparatus could be quite varied in configuration. The key requirements of the power linkage include:
Other arrangements of gears, belts and chain drives that accomplish these requirements are readily apparent to one skilled in the art.
Some of the areas that further design engineering work could improve include:
These are all areas that the improvement would be readily apparent to one skilled in the art and are not integral to the present invention. For that reason, the details are not included in this specification.
REFERENCE NUMERALS OF THE DRAWING-
27 anchor bolts
28 rear support
29 engine rear support
30 front support
33 output shaft
34 engine pulley
35 drive belt
36 input pulley
38 front cover
39 rear cover
40 side cover
42 outlet hose
43 return hose
46 worm output gear
47 chain drive sprocket
48 pressure roller
49 chain idler sprocket
50 water pump
51 transfer chain drive sprocket
52 spacer cylinder
53 support channel A
54 gear case
55 front axle block
56 rear axle block
57 drive chain
58 cleaning block
60 spring bracket
62 support channel C
63 support channel B
65 fan motor with shaft
67 transfer chain driven sprocket
68 worm gear shaft
69 transfer chain
70 sprocket shaft
71 worm pinion
72 inner worm gear bearing
74 worm output seal
75 outer worm gear bearing
76 cabinet/cable lip seal
77 gear case lip seal
78 gear case cover lip seal
79 gear case bearing
80 gear case cover bearing
82 gear case cover
83 gear case lubricant
84 inner sprocket shaft bearing
85 outer sprocket shaft bearing
86 cable link
88 pin link plate
90 cable link
91 cable link
92 cable link
93 cable link
95 adjustment screw
96 collar for roller
97 inner roller bearing
98 outer roller bearing
99 roller shaft
100 Belleville spring
101 pressure roller collar
102 pressure roller collar
103 cable link
104 cable link
105 cable link
106 idler sprocket shaft
107 cable idler wheel
108 idler wheel bracket
110 cable traction apparatus
111 gondola bracket
The base 26 provides support for the various mechanism parts. The anchor bolts 27 affix the base 26 to an immovable object such as earth footings or a building frame. The rear support 28, engine rear support 29 and front support 30 are plate steel members to provide structure support. They are rigidly attached to the base 26.
The engine 31 is an internal combustion device that provides the motive power for the cable traction apparatus. Alternate motive power methods such as an electric, pneumatic or hydraulic motor would be possible. The engine 31 output is directed to the transmission/clutch 32. The transmission/clutch 32 provides speed reduction, reversal, and clutch action to the output shaft 33. The engine pulley 34 is connected to the output shaft 33. The V style belt 35 transfers power from the engine pulley 34 to the input pulley 36.
The cabinet 37 is the main sheet metal enclosure of the apparatus. Additional enclosure parts include the front cover 38, rear cover 39 and side cover 40. All of the covers are attached via screws 41.
Heated coolant is pumped from the engine 31 to the radiator 44 via the pump 50 and outlet hose 42. The coolant exits the radiator 44 and returns to the engine 31 via the return hose 43. The side panel 40 includes a plurality of louvers 45 to facilitate air movement to the radiator 44.
Most of the internal parts in this view have been omitted for clarity. The following are included to provide position and perspective for section views—worm output gear 46, chain drive sprocket 47, pressure roller 48 and chain idler sprocket 49.
Most of the internal parts in this view have been omitted for clarity. The following are included to provide position and perspective for section views—transfer chain drive sprocket 51 and spacer block 52.
The drive belt 35 extends into the cabinet 37 via a cabinet opening that allows belt motion. Support channel A 53, support channel B 63 and support channel C 62 are the main structural elements in the apparatus. Only support channel A 53 is shown in this section view. The gear case 54 houses the worm gear 46.
There are three front axle blocks 55 and three rear axle blocks 56. Only one of each is shown in this section view.
The pressure roller 48 and spacer block 52 in row 1 are identified in this section view. The five rows of pressure rollers are shown.
The chain drive sprocket 47 and chain idler sprocket 49 are shown. They are connected with multiple links of the drive chain 57.
The cleaning block 58 is composed of a flexible porous material and pressed against the drive chain 57. The pressure is caused by the spring bracket 60. The spring bracket 60 is connected to the cleaning block 58 and cabinet 37 via multiple screws 59. The relative motion between the cleaning block 58 and chain drive 57 would remove moisture and grease substances from the chain drive 57. This contaminant removal is desired to maintain a high coefficient of friction between the chain drive 57 and the cable 25. There are three sets of cleaning blocks 58 and spring brackets 60. One for each of the three chain drives 57. Only one is shown in this section view.
The power transmission path of the cable traction apparatus is as follows. Not all of the below components are shown on
There is one worm pinion 71, but it drives three output axis of approximately identical gear train. Steps 5 thru 10 above are repeated on axis A, axis B and axis C.
The cabinet 37 attaches to the three support channels (53, 62, 63) via brackets and screws. These brackets and screws are not shown. The radiator 44, return hose 43, fan motor with shaft 65 and fan 66 are shown. The radiator 44 and fan motor with shaft 65 are attached via brackets and screws to the cabinet 37. These brackets and screws are not shown. In operation, outside air is drawn through louvers 45 and heated at it passes through the radiator 44. The fan motor with shaft 65 is reversible. This allows the air flow to be reversed for warmer outside temperatures. In this situation, no heat would be added to the cabinet 37.
The input pulley 36 rotates on the gear case bearing 79 and the gear case cover bearing 80. The clearance between the input pulley 36 and the cable 25 is shown. This clearance is needed to prevent the input pulley 36 rotation from damaging the cable 25. The worm pinion 71 is press fit to the input pulley 36. The gear case cover 82 is attached to the gear case 54 with several bolts 81. The gear case lip seal 77 and gear case cover lip seal 78 are part of the sealed enclosure that is filled with gear case lubricant 83.
The worm pinion 71 engages the worm gear 46 that rotates with the worm gear shaft 68. The worm gear 46 is press fit to the worm gear shaft 68. Worm gearing is standard engineering design. It provides high gear reduction, a 90 degree change in axis of rotation and requires good lubrication due to the sliding contact of the worm teeth. A unique feature of a worm drive is the ability to have one worm pinion engage several worm gears.
The transfer chain drive sprocket 51 and transfer chain 69 are also shown. Only the axis A components have been labeled. The axis B and axis C components are identical.
The friction surface that contacts the cable 25 is shown as a roller chain cable link 86. The requirements of the friction surface are:
Other friction surface alternatives could include a contoured part attached to a flexible V belt or a wire mesh belt. There are a variety of friction surface materials that meet the above requirements.
Several cable links are mentioned with different reference numbers. These links are identical in shape but in different positions in the mechanism. A specific reference number is used to clarify a link in a particular position.
The pressure roller collar 101 is attached to support channel A with bolt 61. Support channel A 53 has a tapped hole that matches the thread on adjustment screw 95. The adjustment screw 95 pushes on the spacer cylinder 52 that pushes on the collar for roller 96. The inner roller bearing 97 and outer roller bearing 98 are press fit to the collar for roller 96. The pressure roller 48 is press fit to the roller shaft 99 that is free to rotate in the inner roller bearing 97 and outer roller bearing 98.
The collar for roller 96 slides (up and down as shown for axis A) in a pocket in the pressure roller collar 101. Rotation of the adjustment screw 95 causes the pressure roller 48 to move closer or further from the cable 25. The axis A adjustment with the cylinder block 52 is used to center the cable 25 and cable links.
The axis B and axis C components would be identical with one exception. Axis B and axis C utilize a group of Belleville springs 100 rather than the cylinder block 52. Belleville springs are a standard engineering device which exert a high increasing force over a small distance. Only the increasing force action of the Belleville spring would be used, not the snap type action. The Axis B and axis C adjustment screws 95 are used to cause the correct spring force to be applied from the pressure rollers 48 to the cable links.
Note that there is one pressure roller collar 101 for each pressure row. The pressure roller collar 101 is a structural member that contains the reaction forces of the pressure rollers 48 in a row (such as Row 1.) The pressure roller collar 101 could be of one piece construction or several rigidly attached pieces.
Note the position of cable links 103 and 104 relative to the pressure roller 48. The pressure roller 48 at this position potentially would be exerting an excessive stress on the cable 25. Cable links 103 and 104 would pivot slightly due to the high force and the end edge of the cable links would potentially damage the cable 25. The next figure will outline how an adjacent cable link prevents this potential denting damage to the cable 25.
Each row includes three pressure rollers (as shown in
There are two realistic requirements that further reduce this 50% target for cable link area. The mechanism operates more effectively with three rather than two axes. This requires that the cable links be staggered by ⅓, therefore the cable link is not centered under the pressure roller when the other axis is at a joint. Also, clearance must be provided between cable links. The apparatus as shown in
An operator 114 would not necessarily be required inside the container. The unit could be operated remotely or automatically. The container merely holds the payload that is desired to be transported up or down the cable 25.
In any event, the invention is only intended to be limited by the scope of the following claims.
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|U.S. Classification||226/172, 226/195, 104/178, 226/176, 226/190|
|International Classification||B66D3/00, B66B9/02, B65H20/00, B61B7/06, F16L1/12, B66D1/00, B65H23/08|
|Cooperative Classification||B66B9/02, B66D3/003, B61B7/06|
|European Classification||B61B7/06, B66D3/00B, B66B9/02|
|May 1, 2007||CC||Certificate of correction|
|Sep 29, 2009||FPAY||Fee payment|
Year of fee payment: 4
|Nov 15, 2013||REMI||Maintenance fee reminder mailed|
|Apr 4, 2014||LAPS||Lapse for failure to pay maintenance fees|
|May 27, 2014||FP||Expired due to failure to pay maintenance fee|
Effective date: 20140404